U.S. patent number 10,024,385 [Application Number 15/115,953] was granted by the patent office on 2018-07-17 for damper device and starting device.
This patent grant is currently assigned to AISIN AW CO., LTD.. The grantee listed for this patent is AISIN AW CO., LTD.. Invention is credited to Keizo Araki, Yuichiro Hirai, Kazuyoshi Ito, Yuji Kanyama, Kotaro Tsuda, Makoto Ueno, Masaki Wajima.
United States Patent |
10,024,385 |
Ito , et al. |
July 17, 2018 |
Damper device and starting device
Abstract
A damper device has a dynamic damper that includes a mass body
and vibration absorption springs that couple the mass body and an
intermediate member to each other. The vibration absorption springs
are arranged side by side with outer springs in the circumferential
direction. The mass body has spring abutment portions that abut
against end portions of the vibration absorption springs. The
intermediate member has first outer spring abutment portions that
abut against end portions of the outer springs and second outer
spring abutment portions that abut against end portions of the
vibration absorption springs on the radially inner side with
respect to the spring abutment portions. The first outer spring
abutment portions extend toward the radially outer side with
respect to the second outer spring abutment portions.
Inventors: |
Ito; Kazuyoshi (Tsushima,
JP), Araki; Keizo (Hekinan, JP), Ueno;
Makoto (Anjo, JP), Hirai; Yuichiro (Okazaki,
JP), Wajima; Masaki (Anjo, JP), Kanyama;
Yuji (Sabae, JP), Tsuda; Kotaro (Fukui,
JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
AISIN AW CO., LTD. |
Aichi-ken |
N/A |
JP |
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Assignee: |
AISIN AW CO., LTD. (Anjo-shi,
Aichi-ken, JP)
|
Family
ID: |
54008853 |
Appl.
No.: |
15/115,953 |
Filed: |
February 19, 2015 |
PCT
Filed: |
February 19, 2015 |
PCT No.: |
PCT/JP2015/054530 |
371(c)(1),(2),(4) Date: |
August 02, 2016 |
PCT
Pub. No.: |
WO2015/129532 |
PCT
Pub. Date: |
September 03, 2015 |
Prior Publication Data
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Document
Identifier |
Publication Date |
|
US 20170175849 A1 |
Jun 22, 2017 |
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Foreign Application Priority Data
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|
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Feb 28, 2014 [JP] |
|
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2014-039656 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H
45/02 (20130101); F16F 15/12353 (20130101); F16F
15/1428 (20130101); F16F 15/12366 (20130101); F16H
2045/0231 (20130101); F16H 2045/0221 (20130101); F16H
2045/0263 (20130101) |
Current International
Class: |
F16F
15/123 (20060101); F16H 45/02 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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2012-202544 |
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Oct 2012 |
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JP |
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2011/076168 |
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Jun 2011 |
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WO |
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2013/161493 |
|
Oct 2013 |
|
WO |
|
Other References
International Search Report of PCT/JP2015/054530, dated May 19,
2015. [PCT/ISA/210]. cited by applicant .
Written Opinion of PCT/JP2015/054530, dated May 19, 2015.
[PCT/ISA/237]. cited by applicant.
|
Primary Examiner: Manley; Mark A
Attorney, Agent or Firm: Sughrue Mion, PLLC
Claims
The invention claimed is:
1. A damper device that includes a plurality of rotary elements
that include at least an input element and an output element, a
torque transfer elastic body that transfers torque between the
plurality of rotary elements, and a dynamic damper that includes a
mass body and a vibration absorption elastic body that couples the
mass body and one of the plurality of rotary elements to each other
and that damps vibration by applying vibration in the opposite
phase to the one rotary element, wherein: the vibration absorption
elastic body is disposed side by side with the torque transfer
elastic body in a circumferential direction; the mass body has an
elastic body abutment portion that abuts against an end portion of
the vibration absorption elastic body; the one rotary element has a
first abutment portion that abuts against an end portion of the
torque transfer elastic body and a second abutment portion that
abuts against an end portion of the vibration absorption elastic
body on a radially inner side with respect to the elastic body
abutment portion of the mass body; and the first abutment portion
extends toward a radially outer side with respect to the second
abutment portion.
2. The damper device according to claim 1, wherein: torque is
transferred from the input element to the one rotary element via
the torque transfer elastic body; and the input element has an
input abutment portion that abuts against the torque transfer
elastic body on a radially outer side with respect to the first
abutment portion of the one rotary element.
3. The damper device according to claim 2, further comprising: a
rotation restriction stopper that restricts relative rotation
between the input element and the output element, wherein the input
abutment portion is configured to abut against an end portion of
the vibration absorption elastic body on a radially outer side with
respect to the elastic body abutment portion of the mass body
before relative rotation between the input element and the output
element is restricted by the rotation restriction stopper.
4. The damper device according to claim 2, wherein: the plurality
of rotary elements include an intermediate element disposed between
the input element and the output element via the torque transfer
elastic body; and the one rotary element is the intermediate
element.
5. The damper device according to claim 1, wherein a distance from
a rotational axis of the damper device to the elastic body abutment
portion and a distance from the rotational axis to the first
abutment portion are equal to each other.
6. The damper device according to claim 1, wherein: the torque
transfer elastic body includes an outer elastic body that transfers
torque between the input element and the output element and an
inner elastic body disposed on an inner side with respect to the
outer elastic body to transfer torque between the input element and
the output element; and the vibration absorption elastic body is
disposed side by side with the outer elastic body in the
circumferential direction.
7. The damper device according to claim 6, wherein: the inner
elastic body is disposed side by side with the outer elastic body
in a radial direction on the inner side with respect to the outer
elastic body.
8. A starting device that includes the damper device according to
claim 6, a pump impeller, a turbine runner, and a lock-up clutch,
wherein: the mass body is disposed on a side of the turbine runner
with respect to a piston of the lock-up clutch; the input element
has a support portion that extends in parallel with a rotational
axis of the damper device toward the turbine runner so as to
support an inner peripheral portion of the outer elastic body, and
is fixed to the piston of the lock-up clutch; the input abutment
portion of the input element has a tab portion that extends toward
the turbine runner in parallel with the rotational axis; and the
first and second abutment portions and the elastic body abutment
portion are formed to extend from a side of the turbine runner
toward the piston between the support portion of the input element
and the tab portion of the input abutment portion in a radial
direction.
9. The starting device according to claim 8, wherein the turbine
runner is coupled to the mass body.
10. The starting device according to claim 8, wherein the piston
has a support portion that extends from an outer peripheral portion
toward the turbine runner in parallel with the rotational axis to
support at least an outer peripheral portion of the plurality of
outer elastic bodies.
11. The damper device according to claim 3, wherein: the plurality
of rotary elements include an intermediate element disposed between
the input element and the output element via the torque transfer
elastic body; and the one rotary element is the intermediate
element.
12. The damper device according to claim 11, wherein a distance
from a rotational axis of the damper device to the elastic body
abutment portion and a distance from the rotational axis to the
first abutment portion are equal to each other.
13. The damper device according to claim 12, wherein: the torque
transfer elastic body includes an outer elastic body that transfers
torque between the input element and the output element and an
inner elastic body disposed on an inner side with respect to the
outer elastic body to transfer torque between the input element and
the output element; and the vibration absorption elastic body is
disposed side by side with the outer elastic body in the
circumferential direction.
14. The damper device according to claim 13, wherein the inner
elastic body is disposed side by side with the outer elastic body
in a radial direction on the inner side with respect to the outer
elastic body.
15. A starting device that includes the damper device according to
claim 14, a pump impeller, a turbine runner, and a lock-up clutch,
wherein: the mass body is disposed on a side of the turbine runner
with respect to a piston of the lock-up clutch; the input element
has a support portion that extends in parallel with a rotational
axis of the damper device toward the turbine runner so as to
support an inner peripheral portion of the outer elastic body, and
is fixed to the piston of the lock-up clutch; the input abutment
portion of the input element has a tab portion that extends toward
the turbine runner in parallel with the rotational axis; and the
first and second abutment portions and the elastic body abutment
portion are formed to extend from a side of the turbine runner
toward the piston between the support portion of the input element
and the tab portion of the input abutment portion in a radial
direction.
16. The starting device according to claim 15, wherein the turbine
runner is coupled to the mass body.
17. The starting device according to claim 16, wherein the piston
has a support portion that extends from an outer peripheral portion
toward the turbine runner in parallel with the rotational axis to
support at least an outer peripheral portion of the plurality of
outer elastic bodies.
18. The damper device according to claim 2, wherein a distance from
a rotational axis of the damper device to the elastic body abutment
portion and a distance from the rotational axis to the first
abutment portion are equal to each other.
19. The damper device according to claim 4, wherein a distance from
a rotational axis of the damper device to the elastic body abutment
portion and a distance from the rotational axis to the first
abutment portion are equal to each other.
20. The damper device according to claim 4, wherein: the torque
transfer elastic body includes an outer elastic body that transfers
torque between the input element and the output element and an
inner elastic body disposed on an inner side with respect to the
outer elastic body to transfer torque between the input element and
the output element; and the vibration absorption elastic body is
disposed side by side with the outer elastic body in the
circumferential direction.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
This application is a National Stage of International Application
No. PCT/JP2015/054530 filed Feb. 19, 2015, claiming priority based
on Japanese Patent Application No. 2014-039656, filed Feb. 28,
2014, the contents of all of which are incorporated herein by
reference in their entirety.
TECHNICAL FIELD
The present disclosure relates to a damper device that has a
plurality of rotary elements that include at least an input element
and an output element, a torque transfer elastic body that
transfers torque between the plurality of rotary elements, and a
dynamic damper coupled to one of the plurality of rotary elements,
and to a starting device that includes the damper device.
BACKGROUND ART
There has hitherto been known a damper device that includes a first
elastic body that transfers torque between an input element and an
output element, a second elastic body disposed on the inner side of
the first elastic body to transfer torque between the input element
and the output element, and a dynamic damper that has a vibration
absorption elastic body coupled to any of rotary elements that
constitute the damper device and a mass body coupled to the
vibration absorption elastic body (see Patent Document 1, for
example). In the damper device, the vibration absorption elastic
body which constitutes the dynamic damper is disposed on the outer
side or the inner side, in the radial direction, of the first and
second elastic bodies, or between the first elastic body and the
second elastic body in the radial direction.
There has also hitherto been known a fluid transmission apparatus
that includes a pump impeller connected to an input member, a
turbine runner that is rotatable coaxially with the pump impeller,
a damper mechanism connected to an output member, a lock-up clutch
that engages the input member and an input element of the damper
mechanism with each other, an elastic body disposed between the
turbine runner and a first element, which is any one of a plurality
of elements that constitute the damper mechanism, so as to abut
against the turbine runner and the first element, and an engagement
mechanism disposed between the turbine runner and a second element,
which is one of the elements which constitute the damper mechanism
other than the first element, to engage the turbine runner and the
second element with each other so as to rotate together with each
other (see Patent Document 2, for example). In the fluid
transmission apparatus, when the input member and the input element
of the damper mechanism are engaged with each other by the lock-up
clutch, the elastic body constitutes a dynamic damper together with
the turbine runner which serves as a mass that does not contribute
to torque transfer between the input member and the output member.
When the turbine runner and the second element are engaged with
each other by the engagement mechanism to rotate together with each
other, in addition, the elastic body between the turbine runner and
the first element functions as a damper that absorbs torque between
the input member and the output member. Consequently, in the fluid
transmission apparatus, the elastic body between the turbine runner
and the first element can be used as both an elastic body for the
dynamic damper and an elastic body that absorbs excessive torque
input to the input member.
RELATED-ART DOCUMENTS
[Patent Documents]
[Patent Document 1] International Patent Application Publication
No. 2011/076168
[Patent Document 2] Japanese Patent Application Publication No.
2011-214635 (JP 2011-214635 A)
SUMMARY
In the case where the dynamic damper is coupled to one of the
rotary elements which constitute the damper device as in the
example according to the related art described in Patent Document
1, it is necessary to provide an abutment portion that abuts
against an end portion of the vibration absorption elastic body on
the side of the mass body of the dynamic damper, and to provide the
one rotary element with a first abutment portion that abuts against
an end portion of the first or second elastic body for torque
transfer and a second abutment portion that abuts against an end
portion of the vibration absorption elastic body. Unless the three
types of abutment portions are disposed adequately so as not to
interfere with each other, however, the stroke of the elastic
bodies for torque transfer and the stroke of the vibration
absorption elastic body of the dynamic damper may not be secured
well, and the hysteresis of the elastic bodies for torque transfer,
that is, a friction force that acts on the elastic bodies when the
load is reduced, may become large. Meanwhile, Patent Document 2
does not describe at all securing the stroke of the vibration
absorption elastic body of the dynamic damper well or the
hysteresis of the elastic bodies for torque transfer.
It is therefore a main object of the present disclosure to provide
a damper device that includes a dynamic damper, in which the stroke
of torque transfer elastic bodies and the stroke of a vibration
absorption elastic body of the dynamic damper are secured well and
the hysteresis of the torque transfer elastic bodies is
reduced.
The present disclosure provides
a damper device that includes a plurality of rotary elements that
include at least an input element and an output element, a torque
transfer elastic body that transfers torque between the plurality
of rotary elements, and a dynamic damper that includes a mass body
and a vibration absorption elastic body that couples the mass body
and one of the plurality of rotary elements to each other and that
damps vibration by applying vibration in the opposite phase to the
one rotary element, wherein:
the vibration absorption elastic body is disposed side by side with
the torque transfer elastic body in a circumferential
direction;
the mass body has an elastic body abutment portion that abuts
against an end portion of the vibration absorption elastic
body;
the one rotary element has a first abutment portion that abuts
against an end portion of the torque transfer elastic body and a
second abutment portion that abuts against an end portion of the
vibration absorption elastic body on a radially inner side with
respect to the elastic body abutment portion of the mass body;
and
the first abutment portion extends toward a radially outer side
with respect to the second abutment portion.
By causing the second abutment portion of the one rotary element to
abut against an end portion of the vibration absorption elastic
body on the radially inner side with respect to the elastic body
abutment portion of the mass body as in the damper device, it is
possible to secure the strokes of the torque transfer elastic body
and the vibration absorption elastic body which are arranged side
by side in the circumferential direction well without the second
abutment portion and the elastic body abutment portion interfering
with each other. Further, if the first abutment portion of the one
rotary element which abuts against an end portion of the torque
transfer elastic body extends toward the radially outer side with
respect to the second abutment portion which abuts against an end
portion of the vibration absorption elastic body, generally the
center of the end portion of the torque transfer elastic body can
be pushed by the first abutment portion by causing the end portion
of the torque transfer elastic body and the first abutment portion
to abut against each other such that the center of the end portion
of the torque transfer elastic body and the first abutment portion
overlap with each other. Consequently, it is possible to reduce a
hysteresis, that is, a friction force that acts on the torque
transfer elastic body when the load is reduced, by more adequately
expanding and contracting the torque transfer elastic body which
abuts against the first abutment portion along the axis.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic configuration diagram illustrating a starting
device that includes a damper device according to an embodiment of
the present disclosure.
FIG. 2 is a sectional view illustrating the damper device which is
included in the starting device of FIG. 1.
FIG. 3 is a front view illustrating the damper device which is
included in the starting device of FIG. 1.
FIG. 4 is a front view illustrating the damper device which is
included in the starting device of FIG. 1.
FIG. 5 is a schematic diagram illustrating operation of the
starting device of FIG. 1.
FIG. 6 is a schematic diagram illustrating operation of the
starting device of FIG. 1.
FIG. 7 is a chart illustrating the torsional characteristics of the
damper device which is included in the starting device of FIG.
1.
FIG. 8 is a schematic configuration diagram illustrating a starting
device that includes a damper device according to another
embodiment of the present disclosure.
FIG. 9 is a schematic configuration diagram illustrating a starting
device that includes a damper device according to still another
embodiment of the present disclosure.
FIG. 10 is a schematic configuration diagram illustrating a
starting device that includes a damper device according to another
embodiment of the present disclosure.
FIG. 11 is a schematic configuration diagram illustrating a
starting device that includes a damper device according to still
another embodiment of the present disclosure.
FIG. 12 is a schematic configuration diagram illustrating a
starting device that includes a damper device according to another
embodiment of the present disclosure.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENTS
Now, an embodiment of the present disclosure will be described with
reference to the drawings.
FIG. 1 is a schematic configuration diagram illustrating a starting
device 1 that includes a damper device 10 according to an
embodiment of the present disclosure. The starting device 1
illustrated in the drawing is mounted on a vehicle that includes an
engine (internal combustion engine) that serves as a motor. In
addition to the damper device 10, the starting device 1 includes: a
front cover 3 that serves as an input member coupled to a
crankshaft of the engine; a pump impeller (input-side fluid
transmission element) 4 fixed to the front cover 3; a turbine
runner (output-side fluid transmission element) 5 that is coaxially
rotatable with the pump impeller 4; a damper hub 7 that serves as
an output member coupled to the damper device 10 and fixed to an
input shaft IS of a transmission that is an automatic transmission
(AT) or a continuously variable transmission (CVT); a lock-up
clutch 8 which is a single-plate hydraulic clutch; a dynamic damper
20 coupled to the damper device 10; and so forth.
The pump impeller 4 has a pump shell (not illustrated) tightly
fixed to the front cover 3, and a plurality of pump blades (not
illustrated) disposed on the inner surface of the pump shell. The
turbine runner 5 has a turbine shell (not illustrated), and a
plurality of turbine blades (not illustrated) disposed on the inner
surface of the turbine shell. In the embodiment, the inner
peripheral portion of the turbine shell of the turbine runner 5 is
fixed to the damper hub 7 via a plurality of rivets. The pump
impeller 4 and the turbine runner 5 face each other. A stator 6 is
disposed between and coaxially with the pump impeller 4 and the
turbine runner 5. The stator 6 rectifies a flow of working oil
(working fluid) from the turbine runner 5 to the pump impeller 4.
The stator 6 has a plurality of stator blades. The rotational
direction of the stator 6 is set to only one direction by a one-way
clutch 60. The pump impeller 4, the turbine runner 5, and the
stator 6 form a torus (annular flow passage) that allows
circulation of working oil, and function as a torque converter
(fluid transmission apparatus) with a torque amplification
function. It should be noted, however, that the stator 6 and the
one-way clutch 60 may be omitted from the starting device 1, and
that the pump impeller 4 and the turbine runner 5 may function as a
fluid coupling.
The lock-up clutch 8 can establish and release lock-up in which the
front cover 3 and the damper hub 7 are coupled to each other via
the damper mechanism 10. The lock-up clutch 8 has a lock-up piston
80 disposed inside the front cover 3 and in the vicinity of the
inner wall surface of the front cover 3 on the engine side, and
fitted so as to be movable in the axial direction and rotatable
with respect to the damper hub 7. As illustrated in FIG. 2, a
friction material 81 is affixed to a surface of the lock-up piston
80 on the outer peripheral side and on the front cover 3 side. A
lock-up chamber (not illustrated) is defined between the lock-up
piston 80 and the front cover 3. The lock-up chamber is connected
to a hydraulic control device (not illustrated) via a working oil
supply hole and an oil passage formed in the input shaft IS.
Working oil to be supplied from the hydraulic control device to the
pump impeller 4 and the turbine runner 5 (torus) can flow into the
lock-up chamber. Thus, if the pressure in a fluid transmission
chamber 9 defined by the front cover 3 and the pump shell of the
pump impeller 4 and the pressure in the lock-up chamber are kept
equal to each other, the lock-up piston 80 is not moved toward the
front cover 3, and the lock-up piston 80 is not frictionally
engaged with the front cover 3. If the pressure in the lock-up
chamber is decreased by the hydraulic control device (not
illustrated), in contrast, the lock-up piston 80 is moved toward
the front cover 3 by a pressure difference to be frictionally
engaged with the front cover 3. Consequently, the front cover 3 is
coupled to the damper hub 7 via the damper device 10. The lock-up
clutch 8 may be constituted as a multi-plate hydraulic clutch.
As illustrated in FIGS. 1 and 2, the damper device 10 includes: a
drive member (input element) 11, an intermediate member
(intermediate element) 12, and a driven member (output element) 15
as rotary elements; and a plurality of (in the embodiment, two)
outer springs (outer (first) elastic bodies) SP1 disposed in
proximity to the outer periphery of the damper device 10 and a
plurality of (in the embodiment, six) inner springs (inner (second)
elastic bodies) SP2 disposed on the inner side with respect to the
outer springs SP1 as torque transfer elements (torque transfer
elastic bodies).
In the embodiment, the outer springs SP1 are arc coil springs made
of a metal material wound so as to have an axis that extends in an
arc shape when no load is applied. Consequently, the outer springs
SP1 are provided with lower rigidity (a smaller spring constant),
and the damper device 10 is provided with lower rigidity (a longer
stroke). In the embodiment, in addition, the inner springs SP2 are
linear coil springs made of a metal material spirally wound so as
to have an axis that extends straight when no load is applied, and
have higher rigidity (a larger spring constant) than that of the
outer springs SP1. It should be noted, however, that linear coil
springs may be adopted as the outer springs SP1, that arc coil
springs may be adopted as the inner springs SP2, and that springs
that have lower rigidity (a smaller spring constant) than that of
the outer springs SP1 may be adopted as the inner springs SP2.
The drive member 11 is formed in an annular shape, and has: an
annular fixed portion 111 fixed to the lock-up piston 80 of the
lock-up clutch 8 via a plurality of rivets; a plurality of (in the
embodiment, two) spring support portions 112 that extend in the
axial direction from the outer peripheral portion of the fixed
portion 111 toward the pump impeller 4 and the turbine runner 5 and
that support (guide) the inner peripheral portion of the plurality
of outer springs SP1; and a plurality of (in the embodiment, four)
spring abutment portions (input abutment portions) 113 that extend
from the outer peripheral portion of the fixed portion 111 toward
the radially outer side at intervals in the circumferential
direction and that include tab portions 113a that extend in the
axial direction toward the pump impeller 4 and the turbine runner 5
on the radially outer side with respect to the spring support
portions 112. The drive member 11 is fixed to the lock-up piston
80, and disposed in the outer peripheral region in the fluid
transmission chamber 9.
In the embodiment, in addition, the lock-up piston 80 has an
annular spring support portion 80a that supports (guides) the outer
peripheral portion of the plurality of outer springs SP1 and side
portions of the plurality of outer springs SP1 on the turbine
runner 5 side (transmission side) (side portions on the left side
in FIG. 2). The plurality of outer springs SP1 are supported by the
spring support portions 112 of the drive member 11 discussed above
and the spring support portion 80a of the lock-up piston 80, and
disposed in the outer peripheral region in the fluid transmission
chamber 9 in proximity to the outer periphery of the damper device
10. Further, with the damper device 10 attached, as illustrated in
FIG. 3, the spring abutment portions 113 of the drive member 11
abut against end portions of the corresponding outer springs SP1.
That is, two spring abutment portions 113 paired with each other
face each other at an interval that matches the natural length of
the outer springs SP1, for example, and, with the damper device 10
attached, both end portions of each of the outer springs SP1 abut
against the corresponding spring abutment portions 113 of the drive
member 11.
The intermediate member 12 includes: an annular first intermediate
plate member 13 disposed on the side of the pump impeller 4 and the
turbine runner 5; and an annular second intermediate plate member
14 disposed on the lock-up piston 80 (front cover 3) side and
coupled (fixed) to the first intermediate plate member 13 via
rivets.
As illustrated in FIGS. 2 and 3, the first intermediate plate
member 13 which constitutes the intermediate member 12 has: a
plurality of (in the embodiment, six) spring support portions 131
that are arranged side by side at intervals in the circumferential
direction and that support (guide) side portions of the
corresponding inner springs SP2 on the side of the pump impeller 4
and the turbine runner 5 from the outer side; and a plurality of
(in the embodiment, six) spring support portions 132 that are
arranged side by side at intervals in the circumferential direction
on the inner peripheral side of the first intermediate plate member
13 with respect to the plurality of spring support portions 131 and
that support (guide) side portions of the corresponding inner
springs SP2 on the side of the pump impeller 4 and the turbine
runner 5 from the inner side. The first intermediate plate member
13 further has: a plurality of (in the embodiment, four) first
outer spring abutment portions (first abutment portions) 133 that
extend away from the spring support portions 131 toward the
radially outer side at intervals in the circumferential direction
and that include tab portions 133a that extend in the axial
direction toward the lock-up piston 80; and a plurality of (in the
embodiment, six) inner spring abutment portions 134 provided
between the spring support portions 131 and 132 which are adjacent
to each other along the circumferential direction.
As illustrated in FIGS. 2 and 3, the second intermediate plate
member 14 which constitutes the intermediate member 12 has: a
plurality of (in the embodiment, six) spring support portions 141
that are arranged side by side at intervals in the circumferential
direction and that support (guide) side portions of the
corresponding inner springs SP2 on the lock-up piston 80 side from
the outer side; and a plurality of (in the embodiment, six) spring
support portions 142 that are arranged side by side at intervals in
the circumferential direction and that support (guide) side
portions of the corresponding inner springs SP2 on the lock-up
piston 80 side from the inner side. The second intermediate plate
member 14 further has a plurality of (in the embodiment, six) inner
spring abutment portions 144 provided between the spring support
portions 141 and 142 which are adjacent to each other along the
circumferential direction.
When the first and second intermediate plate members 13 and 14 are
coupled to each other, the spring support portions 131 of the first
intermediate plate member 13 face the corresponding spring support
portions 141 of the second intermediate plate member 14, and the
spring support portions 132 of the first intermediate plate member
13 face the corresponding spring support portions 142 of the second
intermediate plate member 14. The plurality of inner springs SP2
are supported by the spring support portions 131 and 141 which face
each other and the spring support portions 132 and 142 which face
each other, arranged side by side with the plurality of outer
springs SP1 in the radial direction (overlap with the plurality of
outer springs SP1 as seen from the radial direction), and disposed
on the inner side with respect to the plurality of outer springs
SP1 in proximity to the input shaft IS.
In addition, with the damper device 10 attached, as illustrated in
FIG. 3, the first outer spring abutment portions 133 of the first
intermediate plate member 13 abut against end portions of the
corresponding outer springs SP1. That is, two first outer spring
abutment portions 133 paired with each other face each other at an
interval that matches the natural length of the outer springs SP1,
for example, and, with the damper device 10 attached, both end
portions of each of the outer springs SP1 abut against the
corresponding first outer spring abutment portions 133 of the first
intermediate plate member 13. In the embodiment, as illustrated in
the drawing, the tab portions 133a of the first outer spring
abutment portions 133 of the first intermediate plate member 13 and
the tab portions 113a of the spring abutment portions 113 of the
drive member 11 are arranged side by side in the radial direction,
and the tab portions 133a of the first outer spring abutment
portions 133 abut against end portions of the corresponding outer
springs SP1 on the radially inner side with respect to the tab
portions 113a of the spring abutment portions 113. Further, the
inner spring abutment portions 134 of the first intermediate plate
member 13 are each provided between the inner springs SP2 which are
adjacent to each other to abut against end portions of two adjacent
the inner springs SP2, and the inner spring abutment portions 144
of the second intermediate plate member 14 are each provided
between the inner springs SP2 which are adjacent to each other to
abut against end portions of the two adjacent inner springs SP2
(see FIG. 2). That is, with the damper device 10 attached, both end
portions of each of the inner springs SP2 abut against the
corresponding inner spring abutment portions 134 and 144 of the
first and second intermediate plate members 13 and 14.
As illustrated in FIG. 2, the driven member 15 is disposed between
the first intermediate plate member 13 and the second intermediate
plate member 14 of the intermediate member 12, and fixed to the
damper hub 7 via a plurality of rivets. In addition, the driven
member 15 has a plurality of (in the embodiment, six) spring
abutment portions 154 formed at intervals in the circumferential
direction to extend toward the radially outer side, and each
disposed between the inner springs SP2 which are adjacent to each
other to abut against end portions of the two adjacent inner
springs SP2. That is, with the damper device 10 attached, both end
portions of each of the inner springs SP2 abut against the
corresponding spring abutment portions 154 of the driven member 15.
Consequently, the driven member 15 is coupled to the drive member
11 via the plurality of outer springs SP1, the intermediate member
12, and the plurality of inner springs SP2.
The damper device 10 further includes, as rotation restriction
stoppers that restrict relative rotation between the drive member
11 and the driven member 15: a first inter-element stopper 16 that
restricts relative rotation between the drive member 11 and the
intermediate member 12; and a second inter-element stopper 17 that
restricts relative rotation between the intermediate member 12 and
the driven member 15. As illustrated in FIG. 2, the first
inter-element stopper 16 is composed of: a stopper portion 114
formed on the drive member 11 by further extending a part of the
spring support portions 112 in the axial direction toward the pump
impeller 4 and the turbine runner 5; and a pair of first outer
spring abutment portions 133 of the first intermediate plate member
13 that face each other via the outer spring SP1. In the
embodiment, two first inter-element stoppers 16 are provided, with
the stopper portion 114 formed in each spring support portion 112
of the drive member 11.
With the damper device 10 attached, as illustrated in FIG. 2, the
stopper portion 114 of the drive member 11 is disposed between a
pair of first outer spring abutment portions 133 of the first
intermediate plate member 13, which face each other via the outer
spring SP1, so as not to abut against the side surfaces of the
first outer spring abutment portions 133. When the stopper portion
114 of the drive member 11 abuts against the side surface of one of
the first outer spring abutment portions 133 on both sides along
with relative rotation between the drive member 11 and the
intermediate member 12, torsion (expansion and contraction) of the
outer springs SP1 and relative rotation between the drive member 11
and the intermediate member 12 are restricted.
The second inter-element stopper 17 is composed of: a stopper
portion 135 that extends in the axial direction from the inner
peripheral portion of the first intermediate plate member 13; and
an arc-shaped opening portion 155 formed in the driven member 15.
In the embodiment, a plurality of second inter-element stoppers 17
are provided by providing a plurality of stopper portions 135 to
the first intermediate plate member 13 and providing a number of
opening portions 155 in the driven member 15, the number being the
same as that of the stopper portions 135. With the damper device 10
attached, as illustrated in FIG. 3, the stopper portion 135 of the
first intermediate plate member 13 is inserted into the
corresponding opening portion 155 of the driven member 15 so as not
to abut against inner wall surfaces on both sides that define the
opening portion 155. As illustrated in FIG. 4, when the stopper
portion 135 on the intermediate member 12 side abuts against one of
the inner wall surfaces of the opening portion 155 positioned on
both sides along with relative rotation between the intermediate
member 12 and the driven member 15, torsion (expansion and
contraction) of the inner springs SP2 and relative rotation between
the intermediate member 12 and the driven member 15 are
restricted.
Consequently, when torsion of the outer springs SP1 and relative
rotation between the drive member 11 and the intermediate member 12
are restricted by the first inter-element stoppers 16 and torsion
of the inner springs SP2 and relative rotation between the
intermediate member 12 and the driven member 15 are restricted by
the second inter-element stoppers 17, relative rotation between the
drive member 11 and the driven member 15 is restricted. In the
embodiment, in addition, the first inter-element stoppers 16 (the
specifications of the drive member 11, the intermediate member 12,
and the outer springs SP1) and the second inter-element stoppers 17
(the specifications of the intermediate member 12, the driven
member 15, and the inner springs SP2) are configured (set) such
that torsion of the inner springs SP2 and relative rotation between
the intermediate member 12 and the driven member 15 are restricted
by the second inter-element stoppers 17 before torsion of the outer
springs SP1 and relative rotation between the drive member 11 and
the intermediate member 12 are restricted by the first
inter-element stoppers 16 along with an increase in input
torque.
The dynamic damper 20 includes: an annular mass body 21; and a
plurality of vibration absorption springs (vibration absorption
elastic bodies) SP3 that are linear coil springs or arc coil
springs (in the embodiment, two linear coil springs) disposed
between the mass body 21 and the intermediate member (first rotary
element) 12 which is a rotary element of the damper device 10. The
"dynamic damper" is a mechanism that damps vibration of a vibrating
body by applying, to the vibrating body, vibration in the opposite
phase at a frequency (engine rotational speed) that coincides with
the resonance frequency of the vibrating body, and is constituted
by coupling a spring (elastic body) and a mass body to the
vibrating body (in the embodiment, the intermediate member 12) such
that the spring and the mass body are not included in the torque
transfer path. That is, vibration at a desired frequency can be
damped by the dynamic damper 20 by adjusting the rigidity of the
vibration absorption springs SP3 and the weight of the mass body
21.
The mass body 21 of the dynamic damper 20 has a plurality of (in
the embodiment, four) spring abutment portions (elastic body
abutment portions) 21a that extend in the axial direction from the
outer peripheral portion at intervals in the circumferential
direction. The plurality of spring abutment portions 21a are formed
symmetrically with respect to the axis of the mass body 21 such
that two (a pair of) spring abutment portions 21a are proximate to
each other. The two spring abutment portions 21a which are paired
with each other face each other at an interval that matches the
natural length of the vibration absorption springs SP3, for
example. In addition, the first intermediate plate member 13 of the
intermediate member 12, to which the dynamic damper 20 is coupled,
has a plurality of (in the embodiment, four) second outer spring
abutment portions (second abutment portions) 136 that extend away
from the spring support portions 131 toward the radially outer side
at intervals in the circumferential direction and that include tab
portions 136a that extend in the axial direction toward the lock-up
piston 80. The plurality of second outer spring abutment portions
136 are formed symmetrically with respect to the axis of the first
intermediate plate member 13 between the first outer spring
abutment portions 133 which are adjacent to each other not via the
outer spring SP1 such that two (a pair of) second outer spring
abutment portions 136 are proximate to each other. The two second
outer spring abutment portions 136 which are paired with each other
face each other at an interval that matches the natural length of
the vibration absorption springs SP3, for example.
With the damper device 10 attached, the vibration absorption
springs SP3 are each supported by a pair of spring abutment
portions 21a, and each disposed between two outer springs SP1 which
are adjacent to each other so as to be arranged side by side with
the outer springs SP1 in the circumferential direction. That is,
both end portions of each of the vibration absorption springs SP3
abut against the corresponding spring abutment portions 21a of the
mass body 21, and the vibration absorption springs SP3 overlap the
outer springs SP1 in both the axial direction and the
circumferential direction of the starting device 1 and the damper
device 10. In this way, with the vibration absorption springs SP3
which constitute the dynamic damper 20 disposed in proximity to the
outer periphery of the damper device 10 so as to be arranged side
by side with the outer springs SP1 in the circumferential
direction, an increase in outside diameter of the damper device 10
can be suppressed to make the entire device compact compared to a
case where the vibration absorption springs SP3 are disposed on the
outer side or the inner side, in the radial direction, of the outer
springs SP1 and the inner springs SP2 or between the outer springs
SP1 and the inner springs SP2 in the radial direction.
In the embodiment, the plurality of outer springs SP1 and the
plurality of vibration absorption springs SP3 are disposed on an
identical circumference (see FIG. 3), and the distance between: the
axis (rotational axis) of the starting device 1 and the damper
device 10; and the axis of the outer springs SP1 and the distance
between: the axis of the starting device 1 and the damper device
10; and the axis of the vibration absorption springs SP3 are equal
to each other. Consequently, it is possible to suppress an increase
in outside diameter of the damper device 10 better. In the
embodiment, in addition, the outer springs SP1 and the vibration
absorption springs SP3 are disposed such that the axes of the outer
springs SP1 and the vibration absorption springs SP3 are included
in an identical plane that is orthogonal to the axis of the
starting device 1 and the damper device 10. Consequently, it is
also possible to suppress an increase in axial length of the damper
device 10. It should be noted, however, that it is not necessary
that the distance between the axis of the damper device 10 and the
axis of the outer springs SP1 and the distance between the axis of
the damper device 10 and the axis of the vibration absorption
springs SP3 need not completely coincide with each other and may be
slightly different from each other because of a design tolerance or
the like. Similarly, the axis of the outer springs SP1 and the axis
of the vibration absorption springs SP3 may not be included in a
completely identical plane, and may be slightly displaced from each
other in the axial direction because of a design tolerance or the
like.
Further, with the damper device 10 attached, both end portions of
each of the vibration absorption springs SP3 abut against the
corresponding second outer spring abutment portions 136 of the
first intermediate plate member 13. In the embodiment, as
illustrated in FIG. 3, the tab portions 136a of the second outer
spring abutment portions 136 of the first intermediate plate member
13 and the spring abutment portions 21a of the mass body 21 are
arranged side by side in the radial direction, and the tab portions
136a of the second outer spring abutment portions 136 abut against
end portions of the corresponding vibration absorption springs SP3
on the radially inner side with respect to the spring abutment
portions 21a of the mass body 21. Consequently, the vibration
absorption springs SP3, that is, the dynamic damper 20, are coupled
to the intermediate member 12 of the damper device 10.
In addition, the dynamic damper 20 (damper device 10) includes a
third inter-element stopper 18 that restricts relative rotation
between the mass body 21 and the first intermediate plate member 13
(intermediate member 12). The third inter-element stopper 18 is
composed of: a stopper portion 137 that extends from the first
intermediate plate member 13 toward the mass body 21; and an
arc-shaped opening portion 210 formed in the mass body 21, for
example. In the embodiment, a plurality of third inter-element
stoppers 18 are provided by providing a plurality of stopper
portions 137 to the first intermediate plate member 13 and
providing a number of opening portions 210 in the mass body 21, the
number being the same as that of the stopper portions 137. With the
damper device 10 attached, the stopper portions 137 of the first
intermediate plate member 13 are inserted into the corresponding
opening portions 210 of the mass body 21 so as not to abut against
inner wall surfaces on both sides that define the opening portions
21o. When the stopper portion 137 of the intermediate member 12
abuts against one of the inner wall surfaces of the opening portion
210 positioned on both sides along with relative rotation between
the first intermediate plate member 13 (intermediate member 12) and
the mass body 21, torsion of the vibration absorption springs SP3
and relative rotation between the mass body 21 and the first
intermediate plate member 13 (intermediate member 12) are
restricted.
In the damper device 10 which includes the dynamic damper 20
discussed above, the drive member 11 (second rotary element) which
is a rotary element to which the dynamic damper 20 is not coupled
is provided with additional abutment portions (additional coupling
portions) 113x that abut against end portions of the vibration
absorption springs SP3 before relative rotation between the drive
member 11 and the driven member 15 is restricted by the first and
second inter-element stoppers 16 and 17. That is, in the drive
member 11 of the damper device 10, a plurality of (in the
embodiment, two) spring abutment portions 113 (which include the
tab portions 113a) that abut against end portions (on the left side
in FIG. 3) of the outer springs SP1 on the downstream side (vehicle
advancing direction side) in the direction (indicated by the arrow
in FIG. 3; hereinafter referred to as "forward rotational
direction") of rotation made when the drive member 11 is rotated by
power from the engine with the damper device 10 attached are
extended in the circumferential direction toward the downstream
side (vehicle advancing direction side) in the forward rotational
direction so as to have a circumferential length that is larger
than the circumferential length required in terms of the strength
or the like. In the embodiment, end portions, on the downstream
side in the forward rotational direction, of the spring abutment
portions 113 which are extended in the circumferential direction in
this way are used as the additional abutment portions 113x.
With the damper device 10 attached, as illustrated in FIG. 3, the
additional abutment portions 113x do not abut against end portions
of the corresponding vibration absorption springs SP3 of the
dynamic damper 20, and can abut against end portions of the
corresponding vibration absorption springs SP3 when the drive
member 11 is rotated in the forward rotational direction with
respect to the intermediate member 12. In the embodiment, the
circumferential length of the two spring abutment portions 113 (the
angle about the axis of the damper device 10 which prescribes the
circumferential length) is determined such that the additional
abutment portions 113x abut against end portions of the
corresponding vibration absorption springs SP3 (see FIG. 4) before
torsion of the outer springs SP1 and relative rotation between the
drive member 11 and the intermediate member 12 are restricted by
the first inter-element stoppers 16 and at the same time as torsion
of the inner springs SP2 and relative rotation between the
intermediate member 12 and the driven member 15 are restricted by
the second inter-element stoppers 17. That is, the angle of
rotation of the drive member 11 with respect to the intermediate
member 12 made before the additional abutment portions 113x abut
against end portions of the corresponding vibration absorption
springs SP3 is smaller than the angle of rotation of the drive
member 11 with respect to the driven member 15 made before relative
rotation is restricted by the first and second inter-element
stoppers 16 and 17.
With the damper device 10 attached, in addition, as illustrated in
FIG. 3, the tab portions 113a which are included in the additional
abutment portions 113x are partially arranged side by side with
(overlap with) the spring abutment portions 21a of the mass body 21
in the radial direction on the radially outer side of the spring
abutment portions 21a. Consequently, with the damper device 10
attached, the tab portions 136a of the second outer spring abutment
portions 136 of the first intermediate plate member 13, the spring
abutment portions 21a of the mass body 21, and the tab portions
113a (end portions) which are included in the additional abutment
portions 113x are arranged side by side in this order from the
inner side toward the outer side. In addition, in the damper device
10, as discussed above, the tab portions 133a of the first outer
spring abutment portions 133 of the first intermediate plate member
13 and the tab portions 113a of the spring abutment portions 113 of
the drive member 11 are arranged side by side in the radial
direction, and the tab portions 133a of the first outer spring
abutment portions 133 abut against end portions of the
corresponding outer springs SP1 on the radially inner side with
respect to the tab portions 113a of the spring abutment portions
113. Consequently, the spring abutment portions 113, that is, the
tab portions 113a of the additional abutment portions 113x, the
spring abutment portions 21a of the mass body 21, and the tab
portions 136a of the second outer spring abutment portions 136 of
the first intermediate plate member 13 can be prevented from
interfering with each other, and the tab portions 113a of the
spring abutment portions 113 of the drive member 11 and the tab
portions 133a of the first outer spring abutment portions 133 of
the first intermediate plate member 13 can be prevented from
interfering with each other. As a result, it is possible to secure
the strokes of the outer springs SP1 and the vibration absorption
springs SP3 which are arranged side by side in the circumferential
direction well.
In the damper device 10, further, the first outer spring abutment
portions 133 which abut against end portions of the outer springs
SP1 and the second outer spring abutment portions 136 which abut
against end portions of the vibration absorption springs SP3 are
disposed in the first intermediate plate member 13 which
constitutes the intermediate member 12 so as to be adjacent to each
other in the circumferential direction. The first outer spring
abutment portions 133 extend toward the radially outer side with
respect to the second outer spring abutment portions 136 which abut
against end portions of the vibration absorption springs SP3 on the
radially inner side with respect to the spring abutment portions
21a of the mass body 21. That is, as illustrated in FIG. 3, the tab
portions 133a of the first outer spring abutment portions 133 are
positioned on the radially outer side with respect to the tab
portions 136a of the second outer spring abutment portions 136.
Consequently, generally the center of the end portions of the outer
springs SP1 can be pushed by the first outer spring abutment
portions 133 by causing the end portions of the outer springs SP1
and the first outer spring abutment portions 133 (tab portions
133a) to abut against each other such that the center of the end
portions of the outer springs SP1 and the tab portions 133a of the
first outer spring abutment portions 133 overlap with each
other.
Next, operation of the starting device 1 configured as discussed
above will be described.
When lock-up is released by the lock-up clutch 8 of the starting
device 1, as seen from FIG. 1, torque (power) transferred from the
engine which serves as a motor to the front cover 3 is transferred
to the input shaft IS of the transmission via a path that includes
the pump impeller 4, the turbine runner 5, and the damper hub 7. In
contrast, when lock-up is established by the lock-up clutch 8 of
the starting device 1, as seen from FIG. 5, torque from the engine
is transferred to the input shaft IS of the speed change device via
a path that includes the front cover 3, the lock-up clutch 8, the
drive member 11, the outer springs SP1, the intermediate member 12,
the inner springs SP2, the driven member 15, and the damper hub 7.
In this event, fluctuations in torque input to the front cover 3
are mainly damped (absorbed) by the outer springs SP1 and the inner
springs SP2 of the damper device 10 which act in series. Thus, in
the starting device 1, when lock-up is established by the lock-up
clutch 8, fluctuations in torque input to the front cover 3 can be
damped (absorbed) well by the damper device 10.
Further, when the intermediate member 12 is rotated by torque from
the engine along with rotation of the engine when lock-up is
established, some (two) of the second outer spring abutment
portions 136 of the first intermediate plate member 13 press first
ends of the corresponding vibration absorption springs SP3, and
second ends of the vibration absorption springs SP3 press one of
the corresponding pair of spring abutment portions 21a of the mass
body 21. As a result, the dynamic damper 20 which includes the mass
body 21 and the plurality of vibration absorption springs SP3 is
coupled to the intermediate member 12 of the damper device 10.
Consequently, in the starting device 1, vibration from the engine
can also be damped (absorbed) by the dynamic damper 20. More
particularly, the overall level of the vibration can be lowered
while providing the vibration with two separate peaks.
In the damper device 10, in addition, the drive member 11 and the
intermediate member 12 rotate relative to each other and the
intermediate member 12 and the driven member 15 rotate relative to
each other in accordance with the magnitude of torque transferred
from the engine to the front cover 3, that is, torque input to the
drive member 11, when lock-up is established. In the embodiment,
when torque input to the drive member 11 reaches a predetermined
value (first value) T1 that is smaller than torque T2 (second
value) that corresponds to a maximum torsional angle .theta.max of
the damper device 10, torsion of the inner springs SP2 and relative
rotation between the intermediate member 12 and the driven member
15 are restricted by the second inter-element stoppers 17, and,
substantially at the same time, the additional abutment portions
113x of the drive member 11 abut against end portions of the
corresponding vibration absorption springs SP3 (end portions on the
upstream side in the forward rotational direction (on the side
opposite to the vehicle advancing direction)) (see FIG. 4). The
torsional angle of the outer springs SP1 corresponding to the angle
of rotation of the drive member 11 with respect to the intermediate
member 12 made before the additional abutment portions 113x abut
against end portions of the vibration absorption springs SP3 is
defined as ".theta.d". The torsional angle of the inner springs SP2
corresponding to the angle of rotation of the intermediate member
12 with respect to the driven member 15 made before relative
rotation is restricted by the second inter-element stoppers 17 is
defined as ".theta.2". The combined spring constant of the
plurality of outer springs SP1 which act in parallel between the
drive member 11 and the intermediate member 12 is defined as "k1".
The combined spring constant of the plurality of inner springs SP2
which act in parallel between the intermediate member 12 and the
driven member 15 is defined as "k2". Then, a relationship
k1.times..theta.d=k2.times..theta.2, that is,
.theta.d=.theta.2.times.k2/k1, is established.
In this way, when the additional abutment portions 113x of the
drive member 11 abut against end portions of the corresponding
vibration absorption springs SP3, the vibration absorption springs
SP3 function as elastic bodies that act in parallel with the
corresponding outer springs SP1 to transfer torque between the
drive member 11 and the intermediate member 12. Consequently, after
torsion of the inner springs SP2 and relative rotation between the
intermediate member 12 and the driven member 15 are restricted by
the second inter-element stoppers 17, as illustrated in FIG. 6,
torque from the engine which serves as a motor is transferred to
the input shaft IS of the speed change device via a path that
includes the front cover 3, the lock-up clutch 8, the drive member
11, the outer springs SP1 and the vibration absorption springs SP3
which act in parallel, the intermediate member 12, the inner
springs SP2, torsion of which has been restricted, and the second
inter-element stoppers 17 (the stopper portions 135 and the opening
portions 155) which are arranged in parallel with the inner springs
SP2, the driven member 15, and the damper hub 7. In this event,
fluctuations in torque input to the front cover 3 are damped
(absorbed) by the outer springs SP1 and the vibration absorption
springs SP3 of the damper device 10 which act in parallel.
As a result, the damper device 10 has the torsional characteristics
illustrated in FIG. 7. That is, the combined spring constant K of
the entire damper device 10 is K=Kf=k1k2/(k1+k2) during a period
(first stage) from the start of transfer of torque from the engine
to the front cover 3 until torque input to the drive member 11
reaches the predetermined value T1 so that the torsional angle of
the damper device 10 (the total torsional angle of the outer
springs SP1 and the inner springs SP2) is brought to a
predetermined angle (threshold) .theta.ref and relative rotation
between the drive member 11 and the driven member 15 is restricted
by the second inter-element stoppers 17. Meanwhile, when the
combined spring constant of the plurality of vibration absorption
springs SP3 which act in parallel between the drive member 11 and
the intermediate member 12 is defined as "k3", the combined spring
constant K of the entire damper device 10 is K=Ks=k1+k3>Kf
during a period (second stage) after relative rotation between the
drive member 11 and the driven member 15 is restricted by the
second inter-element stoppers 17 until torque input to the drive
member 11 reaches the value T2 so that the torsional angle of the
damper device 10 (the total torsional angle of the outer springs
SP1, the inner springs SP2, and the outer springs SP1 and the
vibration absorption springs SP3 which act in parallel) is brought
to the maximum torsional angle .theta.max determined in advance and
relative rotation between the drive member 11 and the intermediate
member 12 is restricted by the first inter-element stoppers 16.
As discussed above, in the damper device 10 which includes the
dynamic damper 20 which is coupled to the intermediate member 12
which serves as a first rotary element, when the additional
abutment portions 113x of the drive member 11 which serves as a
second rotary element abut against end portions of the
corresponding vibration absorption springs SP3 of the dynamic
damper 20, the vibration absorption springs SP3 function as elastic
bodies that transfer torque between the drive member 11 and the
intermediate member 12. Consequently, in the damper device 10, the
rigidity of the inner springs SP2, which do not transfer torque
after the additional abutment portions 113x are coupled to the
vibration absorption springs SP3, can be further lowered, and
torque to be carried by (distributed to) the outer springs SP1
which act in parallel with the vibration absorption springs SP3 can
be reduced to further lower the rigidity of the outer springs SP1.
Thus, it is possible to further lower the rigidity of the damper
device 10 which has the dynamic damper 20.
In addition, the damper device 10 includes the first inter-element
stoppers 16 which restrict relative rotation between the drive
member 11 and the intermediate member 12, and the additional
abutment portions 113x of the drive member 11 abut against end
portions of the corresponding vibration absorption springs SP3
before relative rotation between the drive member 11 and the
intermediate member 12 is restricted by the first inter-element
stoppers 16. Consequently, the outer springs SP1 which are provided
between the drive member 11 and the intermediate member 12 and the
vibration absorption springs SP3 can be caused to act in parallel.
Thus, it is possible to allow input of higher torque to the drive
member 11 after the additional abutment portions 113x abut against
end portions of the corresponding vibration absorption springs SP3
while lowering the rigidity of the entire damper device 10.
In the damper device 10, further, the angle of rotation of the
drive member 11 with respect to the intermediate member 12 made
before the additional abutment portions 113x abut against end
portions of the vibration absorption springs SP3 is determined to
be smaller than the angle of rotation of the drive member 11 with
respect to the driven member 15 made before relative rotation is
restricted by the rotation restriction stoppers. Consequently, it
is possible to cause the additional abutment portions 113x of the
drive member 11 to abut against end portions of the vibration
absorption springs SP3 before relative rotation between the drive
member 11 and the driven member 15 is restricted by the first and
second inter-element stoppers 16 and 17 which serve as the rotation
restriction stoppers.
In addition, the additional abutment portions 113x abut against end
portions of the corresponding vibration absorption springs SP3 when
torque input to the drive member 11 becomes equal to or more than
the predetermined value T1 which is smaller than the torque T2
which corresponds to the maximum torsional angle .theta.max of the
damper device 10. In this way, by causing the vibration absorption
springs SP3 to function as elastic bodies that transfer torque
between the intermediate member 12 and the drive member 11 when
torque input to the drive member 11 has been increased, it is
possible to further lower the rigidity of at least the inner
springs SP2.
Further, the damper device 10 includes, as the rotation restriction
stoppers, the second inter-element stoppers 17 which restrict
relative rotation between the intermediate member 12 and the driven
member (third rotary element) 15 which is coupled to the
intermediate member 12 via the inner springs SP2, and the
additional abutment portions 113x abut against end portions of the
corresponding vibration absorption springs SP3 at the same time as
relative rotation between the intermediate member 12 and the driven
member 15 is restricted by the second inter-element stoppers 17.
Consequently, it is possible to provide the damper device 10 with
two-stage torsional characteristics while lowering the rigidity of
the entire damper device 10. It should be noted, however, that the
additional abutment portions 113x and the second inter-element
stoppers 17 may be configured such that relative rotation between
the intermediate member 12 and the driven member 15 is restricted
after the additional abutment portions 113x abut against end
portions of the corresponding vibration absorption springs SP3.
Consequently, it is possible to provide the damper device 10 with
three-stage torsional characteristics by adjusting the rigidity
(spring constant) of the outer springs SP1, the inner springs SP2,
and the vibration absorption springs SP3.
In addition, in the damper device 10, as discussed above, the tab
portions 113a of the additional abutment portions 113x, the spring
abutment portions 21a of the mass body 21, and the tab portions
136a of the second outer spring abutment portions 136 of the first
intermediate plate member 13 can be prevented from interfering with
each other, and the tab portions 113a of the spring abutment
portions 113 of the drive member 11 and the tab portions 133a of
the first outer spring abutment portions 133 of the first
intermediate plate member 13 can be prevented from interfering with
each other. Thus, it is possible to secure the strokes of the outer
springs SP1 and the vibration absorption springs SP3 which are
arranged side by side in the circumferential direction better.
Further, if the first outer spring abutment portions 133 which abut
against end portions of the outer springs SP1 extend toward the
radially outer side with respect to the second outer spring
abutment portions 136 which abut against end portions of the
vibration absorption springs SP3 as in the damper device 10,
generally the center of the end portions of the outer springs SP1
can be pushed by the first outer spring abutment portions 133 by
causing the end portions of the outer springs SP1 and the first
outer spring abutment portions 133 (tab portions 133a) to abut
against each other such that the center of the end portions of the
outer springs SP1 and the first outer spring abutment portions 133
(tab portions 133a) overlap with each other. Consequently, it is
possible to reduce a hysteresis, that is, a friction force that
acts on the outer springs SP1 when the load is reduced, by more
adequately expanding and contracting the outer springs SP1 which
abut against the first outer spring abutment portions 133 of the
intermediate member 12 along the axis. In the damper device 10,
additionally, torque to be distributed to the outer springs SP1
which are provided between the drive member 11 (input element) and
the intermediate member 12 (one rotary element) can be lowered.
Thus, it is possible to improve the degree of freedom in
arrangement of the first outer spring abutment portions 133 (tab
portions 133a) and the spring abutment portions 113 (tab portions
113a) which are arranged side by side in the radial direction by
reducing the thickness of the first outer spring abutment portions
133 (tab portions 133a) of the intermediate member 12 which abut
against the outer springs SP1 and the thickness of the spring
abutment portions 113 (tab portions 113a) of the drive member
11.
In the damper device 10, the spring abutment portions 113 of the
drive member 11 which abut against end portions of the outer
springs SP1 and the additional abutment portions 113x are formed
integrally with each other. However, the additional abutment
portions 113x may be separated from the spring abutment portions
113, and the additional abutment portions 113x and the spring
abutment portions 113 may be formed to be arranged side by side in
the circumferential direction. In addition, depending on the
rigidity (spring constant) of the outer springs SP1, the inner
springs SP2, and the vibration absorption springs SP3, torsion of
the inner springs SP2 and relative rotation between the
intermediate member 12 and the driven member 15 may be restricted
by the second inter-element stoppers 17 after torsion of the outer
springs SP1 and relative rotation between the drive member 11 and
the intermediate member 12 are restricted by the first
inter-element stoppers 16 so that the inner springs SP2 and the
vibration absorption springs SP3 which serve as elastic bodies that
transfer torque may be caused to act in series after operation of
the first inter-element stoppers 16 and before operation of the
second inter-element stoppers 17. In the damper device 10, further,
the first outer spring abutment portions 133 which abut against end
portions of the outer springs SP1 extend toward the radially outer
side with respect to the second outer spring abutment portions 136
which abut against end portions of the vibration absorption springs
SP3. However, only the first outer spring abutment portions 133
that receive torque from the outer springs SP1 when the drive
member 11 and the intermediate member 12 are rotated in the forward
rotational direction may extend toward the radially outer side with
respect to the second outer spring abutment portions 136.
FIG. 8 is a schematic configuration diagram illustrating a starting
device 1B that includes a damper device 10B according to another
embodiment of the present disclosure. Constituent elements of the
starting device 1B that are identical to the elements of the
starting device 1 discussed above are given the same reference
numerals to omit redundant descriptions.
In the damper device 10B illustrated in FIG. 8, a dynamic damper
20B is coupled to an intermediate member 12B (first rotary
element), and a driven member 15B (second rotary element) is
provided with additional abutment portions 15x that abut against
the vibration absorption springs SP3. In the damper device 10B, in
addition, the first and second inter-element stoppers 16 and 17 are
configured such that torsion of the outer springs SP1 and relative
rotation between the drive member 11 and the intermediate member
12B are restricted by the first inter-element stoppers 16 before
torsion of the inner springs SP2 and relative rotation between the
intermediate member 12B and the driven member 15B are restricted by
the second inter-element stoppers 17 along with an increase in
input torque.
Further, the additional abutment portions 15x of the driven member
15B are configured to abut against end portions of the
corresponding vibration absorption springs SP3 before torsion of
the inner springs SP2 and relative rotation between the
intermediate member 12B and the driven member 15B are restricted by
the second inter-element stoppers 17 and at the same time as
torsion of the outer springs SP1 and relative rotation between the
drive member 11 and the intermediate member 12B are restricted by
the first inter-element stoppers 16. Thus, when the torsional angle
of the inner springs SP2 corresponding to the angle of rotation of
the intermediate member 12B with respect to the driven member 15B
made before the additional abutment portions 15x abut against end
portions of the vibration absorption springs SP3 is defined as
".theta.d" and the torsional angle of the outer springs SP1
corresponding to the angle of rotation of the drive member 11 with
respect to the intermediate member 12B made before relative
rotation is restricted by the first inter-element stoppers 16 is
defined as "01", a relationship
k1.times..theta.1=k2.times..theta.d, that is,
.theta.d=.theta.1.times.k1/k2, is established.
Consequently, in the damper device 10B which includes the dynamic
damper 20B which is coupled to the intermediate member 12B which
serves as a first rotary element, when the additional abutment
portions 15x of the driven member 15B which serves as a second
rotary element abut against end portions of the corresponding
vibration absorption springs SP3 of the dynamic damper 20B, the
vibration absorption springs SP3 function as elastic bodies that
transfer torque between the intermediate member 12B and the driven
member 15. As a result, in the damper device 10B, the rigidity of
the outer springs SP1, which do not transfer torque after the
additional abutment portions 15x are coupled to the vibration
absorption springs SP3, can be further lowered, and torque to be
carried by (distributed to) the inner springs SP2 which act in
parallel with the vibration absorption springs SP3 can be reduced
to further lower the rigidity of the inner springs SP2. Thus, it is
possible to further lower the rigidity of the damper device 10B
which has the dynamic damper 20B.
In addition, the additional abutment portions 15x of the driven
member 15B abut against end portions of the vibration absorption
springs SP3 before relative rotation between the intermediate
member 12B and the driven member 15B is restricted by the second
inter-element stoppers 17. Consequently, the inner springs SP2
which are provided between the intermediate member 12B and the
driven member 15B and the vibration absorption springs SP3 can be
caused to act in parallel. Thus, it is possible to allow input of
higher torque to the drive member 11 after the additional abutment
portions 15x abut against end portions of the corresponding
vibration absorption springs SP3 while lowering the rigidity of the
entire damper device 10B.
In the damper device 10B, further, the angle of rotation of the
intermediate member 12B with respect to the driven member 15B made
before the additional abutment portions 15x abut against end
portions of the vibration absorption springs SP3 is determined to
be smaller than the angle of rotation of the drive member 11 with
respect to the driven member 15B made before relative rotation is
restricted by the first and second inter-element stoppers 16 and
17. Consequently, it is possible to cause the additional abutment
portions 15x of the driven member 15B to abut against end portions
of the vibration absorption springs SP3 before relative rotation
between the drive member 11 and the driven member 15B is restricted
by the first and second inter-element stoppers 16 and 17 which
serve as the rotation restriction stoppers.
In addition, the additional abutment portions 15x of the driven
member 15B abut against end portions of the corresponding vibration
absorption springs SP3 when torque input to the drive member 11
becomes equal to or more than the predetermined value (first value)
which is smaller than the torque which corresponds to the maximum
torsional angle of the damper device 10B. In this way, by causing
the vibration absorption springs SP3 to function as elastic bodies
that transfer torque between the intermediate member 12B and the
driven member 15B when torque input to the drive member 11 has been
increased, it is possible to further lower the rigidity of at least
one of the outer springs SP1 and the inner springs SP2.
Further, the additional abutment portions 15x of the driven member
15B abut against end portions of the corresponding vibration
absorption springs SP3 at the same time as relative rotation
between the drive member 11 and the intermediate member 12B is
restricted by the first inter-element stoppers 16. Consequently, it
is possible to provide the damper device 10B with two-stage
torsional characteristics while lowering the rigidity of the entire
damper device 10B. It should be noted, however, that the additional
abutment portions 15x and the first inter-element stoppers 16 may
be configured such that relative rotation between the drive member
11 and the intermediate member 12B is restricted after the
additional abutment portions 15x abut against end portions of the
corresponding vibration absorption springs SP3. Consequently, it is
possible to provide the damper device 10B with three-stage
torsional characteristics by adjusting the rigidity (spring
constant) of the outer springs SP1, the inner springs SP2, and the
vibration absorption springs SP3.
In the damper device 10B, in addition, the inner springs SP2 and
the vibration absorption springs SP3 may be disposed side by side
in the circumferential direction. Consequently, it is possible to
easily couple the vibration absorption springs SP3 and the turbine
runner 5 which serves as a mass body to each other using a coupling
member, and to reduce a space for arrangement of the coupling
member. Thus, such a configuration is advantageous for a case where
a centrifugal-pendulum vibration absorbing device is coupled to the
damper device 10B in addition to the dynamic damper 20B. In the
damper device 10B, further, the vibration absorption springs SP3
may be configured to act in series with the outer springs SP1, or
both the outer springs SP1 and the inner springs SP2, when the
vibration absorption springs SP3 function as elastic bodies that
transfer torque.
FIG. 9 is a schematic configuration diagram illustrating a starting
device 1C that includes a damper device 10C according to another
embodiment of the present disclosure. Constituent elements of the
starting device 1C that are identical to the elements of the
starting device 1 etc. discussed above are given the same reference
numerals to omit redundant descriptions.
In the damper device 10C illustrated in FIG. 9, a dynamic damper
20C is coupled to a driven member 15C (first rotary element), and
an intermediate member 12C (second rotary element) is provided with
additional abutment portions 12x that abut against the vibration
absorption springs SP3. In the damper device 10C, in addition, the
first and second inter-element stoppers 16 and 17 are configured
such that torsion of the outer springs SP1 and relative rotation
between the drive member 11 and the intermediate member 12C are
restricted by the first inter-element stoppers 16 before torsion of
the inner springs SP2 and relative rotation between the
intermediate member 12C and the driven member 15C are restricted by
the second inter-element stoppers 17 along with an increase in
input torque.
Further, the additional abutment portions 12x of the intermediate
member 12C are configured to abut against end portions of the
corresponding vibration absorption springs SP3 before torsion of
the inner springs SP2 and relative rotation between the
intermediate member 12C and the driven member 15C are restricted by
the second inter-element stoppers 17 and at the same time as
torsion of the outer springs SP1 and relative rotation between the
drive member 11 and the intermediate member 12C are restricted by
the first inter-element stoppers 16. Thus, when the torsional angle
of the inner springs SP2 corresponding to the angle of rotation of
the intermediate member 12C with respect to the driven member 15C
made before the additional abutment portions 12x abut against end
portions of the vibration absorption springs SP3 is defined as
".theta.d" and the torsional angle of the outer springs SP1
corresponding to the angle of rotation of the drive member 11 with
respect to the intermediate member 12C made before relative
rotation is restricted by the first inter-element stoppers 16 is
defined as ".theta.1", a relationship
k1.times..theta.d=k2.times..theta.d, that is,
.theta.d=.theta.1.times.k1/k2, is established.
Consequently, in the damper device 10C which includes the dynamic
damper 20C which is coupled to the driven member 15C which serves
as a first rotary element, when the additional abutment portions
12x of the intermediate member 12C which serves as a second rotary
element abut against end portions of the corresponding vibration
absorption springs SP3 of the dynamic damper 20C, the vibration
absorption springs SP3 function as elastic bodies that transfer
torque between the intermediate member 12C and the driven member
15C. As a result, in the damper device 10C, the rigidity of the
outer springs SP1, which do not transfer torque after the
additional abutment portions 12x are coupled to the vibration
absorption springs SP3, can be further lowered, and torque to be
carried by (distributed to) the inner springs SP2 which act in
parallel with the vibration absorption springs SP3 can be reduced
to further lower the rigidity of the inner springs SP2. Thus, it is
possible to further lower the rigidity of the damper device 10C
which has the dynamic damper 20C.
In addition, the additional abutment portions 12x of the
intermediate member 12C abut against end portions of the vibration
absorption springs SP3 before relative rotation between the
intermediate member 12C and the driven member 15C is restricted by
the second inter-element stoppers 17. Consequently, the inner
springs SP2 which are provided between the intermediate member 12C
and the driven member 15C and the vibration absorption springs SP3
can be caused to act in parallel. Thus, it is possible to allow
input of higher torque to the drive member 11 after the additional
abutment portions 12x abut against end portions of the
corresponding vibration absorption springs SP3 while lowering the
rigidity of the entire damper device 10C.
In the damper device 10C, further, the angle of rotation of the
intermediate member 12C with respect to the driven member 15C made
before the additional abutment portions 12x abut against end
portions of the vibration absorption springs SP3 is determined to
be smaller than the angle of rotation of the drive member 11 with
respect to the driven member 15C made before relative rotation is
restricted by the first and second inter-element stoppers 16 and
17. Consequently, it is possible to cause the additional abutment
portions 12x of the intermediate member 12C to abut against end
portions of the vibration absorption springs SP3 before relative
rotation between the drive member 11 and the driven member 15C is
restricted by the first and second inter-element stoppers 16 and 17
which serve as the rotation restriction stoppers.
In addition, the additional abutment portions 12x of the
intermediate member 12C abut against end portions of the
corresponding vibration absorption springs SP3 when torque input to
the drive member 11 becomes equal to or more than the predetermined
value (first value) which is smaller than the torque which
corresponds to the maximum torsional angle of the damper device
10C. In this way, by causing the vibration absorption springs SP3
to function as elastic bodies that transfer torque between the
intermediate member 12 and the driven member 15C when torque input
to the drive member 11 has been increased, it is possible to
further lower the rigidity of at least one of the outer springs SP1
and the inner springs SP2.
Further, the additional abutment portions 12x of the intermediate
member 12C abut against end portions of the corresponding vibration
absorption springs SP3 at the same time as relative rotation
between the drive member 11 and the intermediate member 12C is
restricted by the first inter-element stoppers 16. Consequently, it
is possible to provide the damper device 10C with two-stage
torsional characteristics while lowering the rigidity of the entire
damper device 10C. It should be noted, however, that the additional
abutment portions 12x and the first inter-element stoppers 16 may
be configured such that relative rotation between the drive member
11 and the intermediate member 12C is restricted after the
additional abutment portions 12x abut against end portions of the
corresponding vibration absorption springs SP3. Consequently, it is
possible to provide the damper device 10C with three-stage
torsional characteristics by adjusting the rigidity (spring
constant) of the outer springs SP1, the inner springs SP2, and the
vibration absorption springs SP3.
Also in the damper device 10C, in addition, the inner springs SP2
and the vibration absorption springs SP3 may be disposed side by
side in the circumferential direction. Consequently, it is possible
to easily couple the vibration absorption springs SP3 and the
turbine runner 5 which serves as a mass body to each other using a
coupling member, and to reduce a space for arrangement of the
coupling member. Thus, such a configuration is advantageous for a
case where a centrifugal-pendulum vibration absorbing device is
coupled to the damper device 10C in addition to the dynamic damper
20C. In the damper device 10C, further, the vibration absorption
springs SP3 may be configured to act in series with the outer
springs SP1, or both the outer springs SP1 and the inner springs
SP2, when the vibration absorption springs SP3 function as elastic
bodies that transfer torque.
FIG. 10 is a schematic configuration diagram illustrating a
starting device 1D that includes a damper device 10D according to
still another embodiment of the present disclosure. Constituent
elements of the starting device 1D that are identical to the
elements of the starting device 1 etc. discussed above are given
the same reference numerals to omit redundant descriptions.
In the damper device 10D illustrated in FIG. 10, a dynamic damper
20D is coupled to a driven member 15D (first rotary element), and a
drive member 11D (second rotary element) is provided with
additional abutment portions 11x that abut against the vibration
absorption springs SP3. In the damper device 10D, in addition, the
first and second inter-element stoppers 16 and 17 are configured
such that one of the first and second inter-element stoppers 16 and
17 restrict relative rotation between two corresponding rotary
elements earlier than the other. Further, the additional abutment
portions 11x of the drive member 11D are configured to abut against
end portions of the corresponding vibration absorption springs SP3
before relative rotation between two rotary elements is restricted
by the other of the first and second inter-element stoppers 16 and
17 and at the same time as relative rotation between two rotary
elements is restricted by the one of the first and inter-element
stoppers 16 and 17.
In the case where the first inter-element stoppers 16 restrict
relative rotation between two rotary elements earlier, the
torsional angle corresponding to the angle of rotation of the drive
member 11D with respect to the driven member 15D made before the
additional abutment portions 11x abut against end portions of the
vibration absorption springs SP3 is defined as ".theta.d", and the
torsional angle of the outer springs SP1 corresponding to the angle
of rotation of the drive member 11D with respect to the
intermediate member 12 made before relative rotation is restricted
by the first inter-element stoppers 16 is defined as ".theta.1".
Then, a relationship .theta.d=.theta.1+.theta.1.times.k1/k2, that
is, .theta.d=.theta.1.times.(k1+k2)/k2, is established. In the case
where the second inter-element stoppers 17 restrict relative
rotation between two rotary elements earlier, meanwhile, the
torsional angle corresponding to the angle of rotation of the drive
member 11D with respect to the driven member 15D made before the
additional abutment portions 11x abut against end portions of the
vibration absorption springs SP3 is defined as ".theta.d", and the
torsional angle of the inner springs SP2 corresponding to the angle
of rotation of the intermediate member 12 with respect to the
driven member 15D made before relative rotation is restricted by
the second inter-element stoppers 17 is defined as ".theta.2".
Then, a relationship .theta.d=.theta.2+.theta.2.times.k2/k1, that
is, .theta.d=.theta.2.times.(k1+k2)/k1, is established.
Consequently, in the damper device 10D which includes the dynamic
damper 20D which is coupled to the driven member 15D which serves
as a first rotary element, when the additional abutment portions
11x of the drive member 11D which serves as a second rotary element
abut against end portions of the corresponding vibration absorption
springs SP3 of the dynamic damper 20D, the vibration absorption
springs SP3 function as elastic bodies that transfer torque between
the drive member 11D and the driven member 15D. As a result, in the
damper device 10D, the rigidity of one of the outer springs SP1 and
the inner springs SP2, which do not transfer torque after the
additional abutment portions 11x are coupled to the vibration
absorption springs SP3, can be further lowered, and torque to be
carried by (distributed to) the other of the outer springs SP1 and
the inner springs SP2 which act in parallel with the vibration
absorption springs SP3 can be reduced to further lower the rigidity
of the other of the outer springs SP1 and the inner springs SP2.
Thus, it is possible to further lower the rigidity of the damper
device 10D which has the dynamic damper 20D.
In addition, the additional abutment portions 11x of the drive
member 11D abut against end portions of the vibration absorption
springs SP3 before relative rotation between the drive member 11D
and the intermediate member 12 is restricted by the first
inter-element stoppers 16 or before relative rotation between the
intermediate member 12 and the driven member 15D is restricted by
the second inter-element stoppers 17. Consequently, the vibration
absorption springs SP3 can be caused to act in parallel with one of
the outer springs SP1 and the inner springs SP2. Thus, it is
possible to allow input of higher torque to the drive member 11D
after the additional abutment portions 11x abut against end
portions of the corresponding vibration absorption springs SP3
while lowering the rigidity of the entire damper device 10D.
In the damper device 10D, further, the angle of rotation of the
drive member 11D with respect to the driven member 15D made before
the additional abutment portions 11x abut against end portions of
the vibration absorption springs SP3 is determined to be smaller
than the angle of rotation of the drive member 11D with respect to
the driven member 15D made before relative rotation is restricted
by the first and second inter-element stoppers 16 and 17.
Consequently, it is possible to cause the additional abutment
portions 11x of the drive member 11D to abut against end portions
of the vibration absorption springs SP3 before relative rotation
between the drive member 11D and the driven member 15D is
restricted by the first and second inter-element stoppers 16 and 17
which serve as the rotation restriction stoppers.
In addition, the additional abutment portions 11x of the drive
member 11D abut against end portions of the corresponding vibration
absorption springs SP3 when torque input to the drive member 11D
becomes equal to or more than the predetermined value (first value)
which is smaller than the torque which corresponds to the maximum
torsional angle of the damper device 10D. In this way, by causing
the vibration absorption springs SP3 to function as elastic bodies
that transfer torque between the drive member 11D and the driven
member 15D when torque input to the drive member 11D has been
increased, it is possible to further lower the rigidity of at least
one of the outer springs SP1 and the inner springs SP2.
Further, the additional abutment portions 11x of the drive member
11D abut against end portions of the corresponding vibration
absorption springs SP3 at the same time as relative rotation
between two rotary elements is restricted by one of the first and
second inter-element stoppers 16 and 17 that operate earlier.
Consequently, it is possible to provide the damper device 10D with
two-stage torsional characteristics while lowering the rigidity of
the entire damper device 10D. It should be noted, however, that the
additional abutment portions 11x and the first and second
inter-element stoppers 16 and 17 may be configured such that
relative rotation between two rotary elements is restricted by one
of the first and second inter-element stoppers 16 and 17 that
operate earlier after the additional abutment portions 11x abut
against end portions of the corresponding vibration absorption
springs SP3. Consequently, it is possible to provide the damper
device 10D with three-stage torsional characteristics by adjusting
the rigidity (spring constant) of the outer springs SP1, the inner
springs SP2, and the vibration absorption springs SP3. In the
damper device 10D, in addition, the vibration absorption springs
SP3 may be disposed side by side in the circumferential direction
with one of the outer springs SP1 and the inner springs SP2.
FIG. 11 is a schematic configuration diagram illustrating a
starting device 1E that includes a damper device 10E according to
still another embodiment of the present disclosure. Constituent
elements of the starting device 1E that are identical to the
elements of the starting device 1 etc. discussed above are given
the same reference numerals to omit redundant descriptions.
In the damper device 10E illustrated in FIG. 11, a dynamic damper
20E is coupled to a drive member 11E (first rotary element), and an
intermediate member 12E (second rotary element) is provided with
additional abutment portions 12x that abut against the vibration
absorption springs SP3. In the damper device 10E, in addition, the
first and second inter-element stoppers 16 and 17 are configured
such that torsion of the inner springs SP2 and relative rotation
between the intermediate member 12E and the driven member 15 are
restricted by the second inter-element stoppers 17 before torsion
of the outer springs SP1 and relative rotation between the drive
member 11E and the intermediate member 12E are restricted by the
first inter-element stoppers 16 along with an increase in input
torque.
Further, the additional abutment portions 12x of the intermediate
member 12E are configured to abut against end portions of the
corresponding vibration absorption springs SP3 before torsion of
the outer springs SP1 and relative rotation between the drive
member 11E and the intermediate member 12E are restricted by the
first inter-element stoppers 16 and at the same time as torsion of
the inner springs SP2 and relative rotation between the
intermediate member 12E and the driven member 15 are restricted by
the second inter-element stoppers 17. Thus, when the torsional
angle of the outer springs SP1 corresponding to the angle of
rotation of the drive member 11E with respect to the intermediate
member 12E made before the additional abutment portions 12x abut
against end portions of the vibration absorption springs SP3 is
defined as ".theta.d" and the torsional angle of the inner springs
SP2 corresponding to the angle of rotation of the intermediate
member 12E with respect to the driven member 15 made before
relative rotation is restricted by the second inter-element
stoppers 17 is defined as ".theta.2", a relationship
k1.times..theta.d=k2.times..theta.2, that is,
.theta.d=.theta.2.times.k2/k1, is established.
Consequently, in the damper device 10E which includes the dynamic
damper 20E which is coupled to the drive member 11E which serves as
a first rotary element, when the additional abutment portions 12x
of the intermediate member 12E which serves as a second rotary
element abut against end portions of the corresponding vibration
absorption springs SP3 of the dynamic damper 20E, the vibration
absorption springs SP3 function as elastic bodies that transfer
torque between the drive member 11E and the intermediate member
12E. As a result, in the damper device 10E, the rigidity of the
inner springs SP2, which do not transfer torque after the
additional abutment portions 12x are coupled to the vibration
absorption springs SP3, can be further lowered, and torque to be
carried by (distributed to) the outer springs SP1 which act in
parallel with the vibration absorption springs SP3 can be reduced
to further lower the rigidity of the outer springs SP1. Thus, it is
possible to further lower the rigidity of the damper device 10E
which has the dynamic damper 20E.
In addition, the additional abutment portions 12x of the
intermediate member 12E abut against end portions of the vibration
absorption springs SP3 before relative rotation between the drive
member 11E and the intermediate member 12E is restricted by the
first inter-element stoppers 16. Consequently, the inner springs
SP2 which are provided between the drive member 11E and the
intermediate member 12E and the vibration absorption springs SP3
can be caused to act in parallel. Thus, it is possible to allow
input of higher torque to the drive member 11 after the additional
abutment portions 12x abut against end portions of the
corresponding vibration absorption springs SP3 while lowering the
rigidity of the entire damper device 10E.
In the damper device 10E, further, the angle of rotation of the
drive member 11E with respect to the intermediate member 12E made
before the additional abutment portions 12x abut against end
portions of the vibration absorption springs SP3 is determined to
be smaller than the angle of rotation of the drive member 11E with
respect to the driven member 15 made before relative rotation is
restricted by the first and second inter-element stoppers 16 and
17. Consequently, it is possible to cause the additional abutment
portions 12x of the intermediate member 12E to abut against end
portions of the vibration absorption springs SP3 before relative
rotation between the drive member 11E and the driven member 15 is
restricted by the first and second inter-element stoppers 16 and 17
which serve as the rotation restriction stoppers.
In addition, the additional abutment portions 12x of the
intermediate member 12E abut against end portions of the
corresponding vibration absorption springs SP3 when torque input to
the drive member 11E becomes equal to or more than the
predetermined value (first value) which is smaller than the torque
which corresponds to the maximum torsional angle of the damper
device 10E. In this way, by causing the vibration absorption
springs SP3 to function as elastic bodies that transfer torque
between the drive member 11E and the intermediate member 12E when
torque input to the drive member 11E has been increased, it is
possible to further lower the rigidity of at least one of the outer
springs SP1 and the inner springs SP2.
Further, the additional abutment portions 12x of the intermediate
member 12E abut against end portions of the corresponding vibration
absorption springs SP3 at the same time as relative rotation
between the intermediate member 12E and the driven member 15 is
restricted by the second inter-element stoppers 17. Consequently,
it is possible to provide the damper device 10E with two-stage
torsional characteristics while lowering the rigidity of the entire
damper device 10E. It should be noted, however, that the additional
abutment portions 12x and the second inter-element stoppers 17 may
be configured such that relative rotation between the intermediate
member 12E and the driven member 15 is restricted after the
additional abutment portions 12x abut against end portions of the
corresponding vibration absorption springs SP3. Consequently, it is
possible to provide the damper device 10E with three-stage
torsional characteristics by adjusting the rigidity (spring
constant) of the outer springs SP1, the inner springs SP2, and the
vibration absorption springs SP3. Also in the damper device 10E, in
addition, the outer springs SP1 and the vibration absorption
springs SP3 may be disposed side by side in the circumferential
direction. In the damper device 10E, further, the vibration
absorption springs SP3 may be configured to act in series with the
outer springs SP1, or both the outer springs SP1 and the inner
springs SP2, when the vibration absorption springs SP3 function as
elastic bodies that transfer torque.
FIG. 12 is a schematic configuration diagram illustrating a
starting device 1F that includes a damper device 10F according to
still another embodiment of the present disclosure. Constituent
elements of the starting device 1F that are identical to the
elements of the starting device 1 etc. discussed above are given
the same reference numerals to omit redundant descriptions.
In the damper device 10F illustrated in FIG. 12, a dynamic damper
20F is coupled to a drive member 11F (first rotary element), and a
driven member 15F (second rotary element) is provided with
additional abutment portions 15x that abut against the vibration
absorption springs SP3. In the damper device 10F, in addition, the
first and second inter-element stoppers 16 and 17 are configured
such that one of the first and second inter-element stoppers 16 and
17 restrict relative rotation between two corresponding rotary
elements earlier than the other. Further, the additional abutment
portions 15x of the driven member 15F are configured to abut
against end portions of the corresponding vibration absorption
springs SP3 before relative rotation between two rotary elements is
restricted by the other of the first and second inter-element
stoppers 16 and 17 and at the same time as relative rotation
between two rotary elements is restricted by the one of the first
and inter-element stoppers 16 and 17.
In the case where the first inter-element stoppers 16 restrict
relative rotation between two rotary elements earlier, the
torsional angle corresponding to the angle of rotation of the drive
member 11F with respect to the driven member 15F made before the
additional abutment portions 15x abut against end portions of the
vibration absorption springs SP3 is defined as ".theta.d", and the
torsional angle of the outer springs SP1 corresponding to the angle
of rotation of the drive member 11F with respect to the
intermediate member 12 made before relative rotation is restricted
by the first inter-element stoppers 16 is defined as ".theta.1".
Then, a relationship .theta.d=.theta.1+.theta.1.times.k1/k2, that
is, .theta.d=.theta.1.times.(k1+k2)/k2, is established. In the case
where the second inter-element stoppers 17 restrict relative
rotation between two rotary elements earlier, meanwhile, the
torsional angle corresponding to the angle of rotation of the drive
member 11F with respect to the driven member 15F made before the
additional abutment portions 15x abut against end portions of the
vibration absorption springs SP3 is defined as ".theta.d", and the
torsional angle of the inner springs SP2 corresponding to the angle
of rotation of the intermediate member 12 with respect to the
driven member 15F made before relative rotation is restricted by
the second inter-element stoppers 17 is defined as ".theta.2".
Then, a relationship .theta.d=.theta.2+.theta.2.times.k2/k1, that
is, .theta.d=.theta.2.times.(k1+k2)/k1, is established.
Consequently, in the damper device 10F which includes the dynamic
damper 20F which is coupled to the drive member 11F which serves as
a first rotary element, when the additional abutment portions 15x
of the driven member 15F which serves as a second rotary element
abut against end portions of the corresponding vibration absorption
springs SP3 of the dynamic damper 20F, the vibration absorption
springs SP3 function as elastic bodies that transfer torque between
the drive member 11F and the driven member 15F. As a result, in the
damper device 10F, the rigidity of one of the outer springs SP1 and
the inner springs SP2, which do not transfer torque after the
additional abutment portions 15x are coupled to the vibration
absorption springs SP3, can be further lowered, and torque to be
carried by (distributed to) the other of the outer springs SP1 and
the inner springs SP2 which act in parallel with the vibration
absorption springs SP3 can be reduced to further lower the rigidity
of the other of the outer springs SP1 and the inner springs SP2.
Thus, it is possible to further lower the rigidity of the damper
device 10F which has the dynamic damper 20F.
In addition, the additional abutment portions 15x of the driven
member 15F abut against end portions of the vibration absorption
springs SP3 before relative rotation between the drive member 11F
and the intermediate member 12 is restricted by the first
inter-element stoppers 16 or before relative rotation between the
intermediate member 12 and the driven member 15F is restricted by
the second inter-element stoppers 17. Consequently, the vibration
absorption springs SP3 can be caused to act in parallel with one of
the outer springs SP1 and the inner springs SP2. Thus, it is
possible to allow input of higher torque to the drive member 11F
after the additional abutment portions 15x abut against end
portions of the corresponding vibration absorption springs SP3
while lowering the rigidity of the entire damper device 10F.
In the damper device 10F, further, the angle of rotation of the
drive member 11F with respect to the driven member 15F made before
the additional abutment portions 15x abut against end portions of
the vibration absorption springs SP3 is determined to be smaller
than the angle of rotation of the drive member 11F with respect to
the driven member 15F made before relative rotation is restricted
by the first and second inter-element stoppers 16 and 17.
Consequently, it is possible to cause the additional abutment
portions 15x of the driven member 15F to abut against end portions
of the vibration absorption springs SP3 before relative rotation
between the drive member 11F and the driven member 15F is
restricted by the first and second inter-element stoppers 16 and 17
which serve as the rotation restriction stoppers.
In addition, the additional abutment portions 15x of the driven
member 15F abut against end portions of the corresponding vibration
absorption springs SP3 when torque input to the drive member 11F
becomes equal to or more than the predetermined value (first value)
which is smaller than the torque which corresponds to the maximum
torsional angle of the damper device 10F. In this way, by causing
the vibration absorption springs SP3 to function as elastic bodies
that transfer torque between the drive member 11F and the driven
member 15F when torque input to the drive member 11F has been
increased, it is possible to further lower the rigidity of at least
one of the outer springs SP1 and the inner springs SP2.
Further, the additional abutment portions 15x of the driven member
15F abut against end portions of the corresponding vibration
absorption springs SP3 at the same time as relative rotation
between two rotary elements is restricted by one of the first and
second inter-element stoppers 16 and 17 that operate earlier.
Consequently, it is possible to provide the damper device 10F with
two-stage torsional characteristics while lowering the rigidity of
the entire damper device 10F. It should be noted, however, that the
additional abutment portions 15x and the first and second
inter-element stoppers 16 and 17 may be configured such that
relative rotation between two rotary elements is restricted by one
of the first and second inter-element stoppers 16 and 17 that
operate earlier after the additional abutment portions 15x abut
against end portions of the corresponding vibration absorption
springs SP3. Consequently, it is possible to provide the damper
device 10F with three-stage torsional characteristics by adjusting
the rigidity (spring constant) of the outer springs SP1, the inner
springs SP2, and the vibration absorption springs SP3. In the
damper device 10F, in addition, the vibration absorption springs
SP3 may be disposed side by side in the circumferential direction
with one of the outer springs SP1 and the inner springs SP2.
The dynamic damper 20 to 20F of the damper device 10 to 10F may be
configured to include the turbine runner 5 as a mass body. In this
case, the mass body 21 discussed above may be altered so as to
function as a coupling member that couples the vibration absorption
springs SP3 and the turbine runner 5 to each other. In addition,
the damper device 10 to 10F may be configured to include a
plurality of intermediate members (intermediate elements), a torque
transfer elastic body disposed between the drive member and one of
the plurality of intermediate members, and a torque transfer
elastic body that has rigidity that is the same as or different
from that of the torque transfer elastic body and that is disposed
between the plurality of intermediate members. Further, the damper
device 10 to 10F may be configured not to include the intermediate
member 12 etc. In the damper device 10 to 10F, the additional
abutment portions 113x, 11x, 12x, 15x are all configured to
directly abut against the corresponding end portions of the
vibration absorption springs SP3. However, the present disclosure
is not limited thereto. That is, the additional abutment portions
113x, 11x, 12x, 15x may be configured to be coupled to the
corresponding end portions of the vibration absorption springs SP3
(indirectly) via other spring abutment portions (tab portions, e.g.
the spring abutment portions 215 of the coupling member 210) or the
like. Further, the starting device 1 to 1F may be configured not to
include a fluid transmission apparatus.
As has been described above, the present disclosure provides a
damper device that includes a plurality of rotary elements that
include at least an input element and an output element, a torque
transfer elastic body that transfers torque between the plurality
of rotary elements, and a dynamic damper that includes a mass body
and a vibration absorption elastic body that couples the mass body
and one of the plurality of rotary elements to each other and that
damps vibration by applying vibration in the opposite phase to the
one rotary element, wherein: the vibration absorption elastic body
is disposed side by side with the torque transfer elastic body in a
circumferential direction; the mass body has an elastic body
abutment portion that abuts against an end portion of the vibration
absorption elastic body; the one rotary element has a first
abutment portion that abuts against an end portion of the torque
transfer elastic body and a second abutment portion that abuts
against an end portion of the vibration absorption elastic body on
a radially inner side with respect to the elastic body abutment
portion of the mass body; and the first abutment portion extends
toward a radially outer side with respect to the second abutment
portion.
In the damper device, the vibration absorption elastic body which
constitutes the dynamic damper is disposed side by side with the
torque transfer elastic body in the circumferential direction. In
addition, the mass body has the elastic body abutment portion which
abuts against an end portion of the vibration absorption elastic
body, and the one rotary element has the first abutment portion
which abuts against an end portion of the torque transfer elastic
body and the second abutment portion which abuts against an end
portion of the vibration absorption elastic body. The second
abutment portion abuts against an end portion of the vibration
absorption elastic body on the radially inner side with respect to
the elastic body abutment portion of the mass body, and the first
abutment portion extends toward the radially outer side with
respect to the second abutment portion.
In this way, by causing the second abutment portion of the one
rotary element to abut against an end portion of the vibration
absorption elastic body on the radially inner side with respect to
the elastic body abutment portion of the mass body, it is possible
to secure the strokes of the torque transfer elastic body and the
vibration absorption elastic body which are arranged side by side
in the circumferential direction well without the second abutment
portion and the elastic body abutment portion interfering with each
other. Further, if the first abutment portion of the one rotary
element which abuts against an end portion of the torque transfer
elastic body extends toward the radially outer side with respect to
the second abutment portion which abuts against an end portion of
the vibration absorption elastic body, generally the center of the
end portion of the torque transfer elastic body can be pushed by
the first abutment portion by causing the end portion of the torque
transfer elastic body and the first abutment portion to abut
against each other such that the center of the end portion of the
torque transfer elastic body and the first abutment portion overlap
with each other. Consequently, it is possible to reduce a
hysteresis, that is, a friction force that acts on the torque
transfer elastic body when the load is reduced, by more adequately
expanding and contracting the torque transfer elastic body which
abuts against the first abutment portion along the axis.
In addition, torque may be transferred from the input element to
the one rotary element via the torque transfer elastic body; and
the input element may have an input abutment portion that abuts
against the torque transfer elastic body on a radially outer side
with respect to the first abutment portion of the one rotary
element.
In this way, by causing the input abutment portion of the input
element which abuts against an end portion of the torque transfer
elastic body to abut against the torque transfer elastic body on
the radially outer side with respect to the first abutment portion
of the one rotary element, it is possible to secure the strokes of
the torque transfer elastic body and the vibration absorption
elastic body which are arranged side by side in the circumferential
direction well without the input abutment portion and the first
abutment portion interfering with each other.
The damper device may further include a rotation restriction
stopper that restricts relative rotation between the input element
and the output element; and the input abutment portion may be
configured to abut against an end portion of the vibration
absorption elastic body on a radially outer side with respect to
the elastic body abutment portion of the mass body before relative
rotation between the input element and the output element is
restricted by the rotation restriction stopper.
Consequently, when the input abutment portion of the input element
abuts against an end portion of the vibration absorption elastic
body of the dynamic damper, the vibration absorption elastic body
functions as an elastic body that transfers torque between the
input element and the one rotary element. As a result, in the
damper device, it is possible to reduce at least torque to be
carried by (distributed to) the torque transfer elastic body which
is provided between the input element and the one rotary element,
and the rigidity of the damper device which has the dynamic damper
can be further reduced by lowering the rigidity of the torque
transfer elastic body. In addition, by disposing the input abutment
portion of the input element, the elastic body abutment portion of
the mass body, and the second abutment portion of the one rotary
element side by side in the radial direction as in the damper
device, it is possible to eliminate interference among the abutment
portions, and to secure the strokes of the torque transfer elastic
body and the vibration absorption elastic body which are arranged
side by side in the circumferential direction better. By lowering
torque to be distributed to the torque transfer elastic body which
is provided between the input element and the one rotary element,
further, it is possible to reduce the thickness of the first
abutment portion of the one rotary element which abuts against the
torque transfer elastic body and the input abutment portion of the
input element, thereby improving the degree of freedom in
arrangement of the first abutment portion and the input abutment
portion which are arranged side by side in the radial
direction.
In addition, the plurality of rotary elements may include an
intermediate element disposed between the input element and the
output element via the torque transfer elastic body; and the one
rotary element may be the intermediate element.
Further, a distance from a rotational axis of the damper device to
(the outer peripheral surface of) the elastic body abutment portion
and a distance from the rotational axis to (the outer peripheral
surface of) the first abutment portion may be equal to each
other.
In addition, the torque transfer elastic body may include an outer
elastic body that transfers torque between the input element and
the output element and an inner elastic body disposed on an inner
side with respect to the outer elastic body to transfer torque
between the input element and the output element; and the vibration
absorption elastic body may be disposed side by side with the outer
elastic body in the circumferential direction. Consequently, it is
possible to make the entire device compact by suppressing an
increase in outside diameter of the damper device compared to a
case where the vibration absorption elastic body which constitutes
the dynamic damper is disposed on the outer side or the inner side
in the radial direction with respect to the outer elastic body or
the inner elastic body or between the outer elastic body and the
inner elastic body in the radial direction.
The present disclosure also provides a starting device that
includes the damper device discussed above, a pump impeller, a
turbine runner, and a lock-up clutch, wherein: the mass body is
disposed on a side of the turbine runner with respect to a piston
of the lock-up clutch; the input element has a support portion that
extends in parallel with a rotational axis of the damper device
toward the turbine runner so as to support an inner peripheral
portion of the outer elastic body, and is fixed to the piston of
the lock-up clutch; the input abutment portion of the input element
has a tab portion that extends toward the turbine runner in
parallel with the rotational axis; and the first and second
abutment portions and the elastic body abutment portion are formed
to extend from a side of the turbine runner toward the piston
between the support portion of the input element and the tab
portion of the input abutment portion in a radial direction.
In addition, the turbine runner may be coupled to the mass
body.
Further, the piston may have a support portion that extends from an
outer peripheral portion toward the turbine runner in parallel with
the rotational axis to support at least an outer peripheral portion
of the plurality of outer elastic bodies.
The present disclosure is not limited to the embodiments described
above in any way, and it is a matter of course that the present
disclosure may be modified in various ways within the broad scope
of the present disclosure. Further, the mode for carrying out the
present disclosure described above is merely a specific form of the
subject matter, and is not limited thereto.
The present disclosure can be utilized, for example, in the field
of manufacture of damper devices or the like.
* * * * *